JPS62261865A - Heat pump device - Google Patents
Heat pump deviceInfo
- Publication number
- JPS62261865A JPS62261865A JP10467986A JP10467986A JPS62261865A JP S62261865 A JPS62261865 A JP S62261865A JP 10467986 A JP10467986 A JP 10467986A JP 10467986 A JP10467986 A JP 10467986A JP S62261865 A JPS62261865 A JP S62261865A
- Authority
- JP
- Japan
- Prior art keywords
- heat pump
- heat
- heat source
- air
- boiling point
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000002918 waste heat Substances 0.000 claims description 43
- 238000009835 boiling Methods 0.000 claims description 25
- 239000003507 refrigerant Substances 0.000 claims description 25
- 238000010438 heat treatment Methods 0.000 description 11
- 230000007423 decrease Effects 0.000 description 5
- 238000001704 evaporation Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 241001122767 Theaceae Species 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 239000002912 waste gas Substances 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
- 239000002351 wastewater Substances 0.000 description 1
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Central Heating Systems (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】 （産業上の利用分野） 本発明はヒートポンプ装置に関する。[Detailed description of the invention] (Industrial application field) The present invention relates to a heat pump device.
（従来の技術及びその問題点）
従来のヒートポンプ装置の１例が第２図に示され、Ｒ１
１４等の高沸点冷媒を圧縮機１、凝縮器２、絞り装置３
、蒸発器４の順に循環させることにより、蒸発器４で温
廃水や廃ガス等の廃熱５が保有する熱を汲み上げ、凝縮
器２から熱を取り出して負荷６に供給する。(Prior art and its problems) An example of a conventional heat pump device is shown in FIG.
A high boiling point refrigerant such as
, evaporator 4 in this order, the evaporator 4 pumps up the heat held by waste heat 5 such as hot waste water or waste gas, extracts the heat from the condenser 2, and supplies it to the load 6.
このヒートポンプ装置では熱源となる廃熱５の贅が不足
する場合にはヒートポンプの能力、成績係数が低下する
ので負荷６に熱を安定して供給できない。In this heat pump device, if there is insufficient waste heat 5 to serve as a heat source, the capacity and coefficient of performance of the heat pump will decrease, making it impossible to stably supply heat to the load 6.
そこで、第３図に示すように、Ｒ１１４等の高沸点冷媒
を用いた高温ヒートポンプ２０とＲ１２、Ｒ２２等の低
沸点冷媒を用いた低温ヒートポンプ３０を組み合わせた
カスケード型ヒートポンプＶ装置が提案された。このカ
スケード型ヒートポンプ装置においては、高沸点冷媒を
圧縮機２１、凝縮器２２、絞り装置２３、蒸発器２４の
順に循環させると同時に低沸点冷媒を圧縮機３１、蒸発
器２４を兼ねる凝縮器３２、絞り装置３３、蒸発器３４
の順に循環させる。そして、蒸発器３４で空気から熱を
汲み上げ、ｙ発器２４を兼ねる凝縮器３２で低沸点冷媒
から貰沸点冷媒に熱を伝達することによって低沸点冷媒
を凝縮させると同時に高沸点冷媒を蒸発させ、この高沸
点冷媒を凝縮器２２で凝縮させることにより熱を取り出
して負荷２５に供給する。Therefore, as shown in FIG. 3, a cascade type heat pump V device has been proposed which combines a high temperature heat pump 20 using a high boiling point refrigerant such as R114 and a low temperature heat pump 30 using a low boiling point refrigerant such as R12 or R22. In this cascade type heat pump device, high boiling point refrigerant is circulated in the order of compressor 21, condenser 22, expansion device 23, and evaporator 24, while low boiling point refrigerant is circulated through compressor 31, condenser 32 which also serves as evaporator 24, Squeezing device 33, evaporator 34
Circulate in this order. Then, the evaporator 34 pumps up heat from the air, and the condenser 32, which also serves as the generator 24, transfers heat from the low boiling point refrigerant to the low boiling point refrigerant, thereby condensing the low boiling point refrigerant and evaporating the high boiling point refrigerant at the same time. By condensing this high boiling point refrigerant in the condenser 22, heat is extracted and supplied to the load 25.
このカスケード型ヒートポンプ装置は空気を熱源として
いるので安定した運転が可能であるが総合成績係数が低
（なり、経済的な運転ができない。This cascade type heat pump device uses air as its heat source, so it can operate stably, but the overall coefficient of performance is low (so it cannot be operated economically).
そこで上記に対処するため、本発明者等は、第４図に示
すように、高沸点冷媒を用いた廃熱源式高温ヒートポン
プ４０の廃熱を熱源とする蒸発器４４と直列に補助蒸発
器４５を設けるとともにこの補助蒸発器４５の熱源とな
る低沸点冷媒を用いた空気熱源式低温ヒートポンプ５０
を設け、前記廃熱量に応じて前記空気熱源式低温ヒート
ポンプ５０を運転するようにしたヒートポンプ装置を提
案した。（特願昭６１−６７２９０号）
第４図において、４０はＲ１１４等の高沸点冷媒を用い
た廃熱源式高温ヒートポンプで、圧縮［４１、凝縮器４
２、絞り装置４３、廃熱４６を熱源とする蒸発器４４、
補助蒸発器４５からなる。５０はＲ１２、Ｒ２２等の低
沸点冷媒を用いた空気熱源式低温ヒートポンプで、圧縮
機５１、補助蒸発器４５を兼ねる凝縮器５２、絞り装置
５３、空気を熱源とする蒸発器５４、凝縮器５２の前後
に配置された開閉弁５５．５６からなる。Therefore, in order to deal with the above problem, the present inventors installed an auxiliary evaporator 45 in series with an evaporator 44 whose heat source is the waste heat of a waste heat source type high temperature heat pump 40 using a high boiling point refrigerant, as shown in FIG. An air heat source type low-temperature heat pump 50 using a low boiling point refrigerant is provided and serves as a heat source for this auxiliary evaporator 45.
We have proposed a heat pump device in which the air heat source type low temperature heat pump 50 is operated according to the amount of waste heat. (Patent Application No. 61-67290) In Fig. 4, 40 is a waste heat source type high temperature heat pump using a high boiling point refrigerant such as R114, compressor [41], condenser 4
2, a throttle device 43, an evaporator 44 using waste heat 46 as a heat source;
It consists of an auxiliary evaporator 45. 50 is an air source type low temperature heat pump using a low boiling point refrigerant such as R12 or R22, which includes a compressor 51, a condenser 52 which also serves as an auxiliary evaporator 45, a throttle device 53, an evaporator 54 using air as a heat source, and a condenser 52. It consists of on-off valves 55 and 56 placed before and after the.
廃熱量が十分であるときは開閉弁５５．５６を閉とし圧
縮機５１を停止することによって空気熱源式低温ヒート
ポンプ５０の運転を止め、圧縮機４１を駆動することに
よって廃熱源式に？ＩＡヒートポンプ４０を運転する。When the amount of waste heat is sufficient, the operation of the air heat source type low temperature heat pump 50 is stopped by closing the on-off valves 55 and 56 and stopping the compressor 51, and the operation of the air heat source type low temperature heat pump 50 is stopped by driving the compressor 41. The IA heat pump 40 is operated.
廃熱１４６の量が十分でない場合には、開閉弁５５．５
６を開として圧縮機５１を駆動して空気熱源式低温ヒー
トポンプ５０を運転すると同時に圧縮［４１を駆動して
廃熱源式高温ヒートポンプ４０を運転する。If the amount of waste heat 146 is not sufficient, the on-off valve 55.5
6 is opened and the compressor 51 is driven to operate the air heat source type low temperature heat pump 50, and at the same time, the compressor 41 is driven to operate the waste heat source type high temperature heat pump 40.
このヒートポンプ装置においては、廃熱４６の量が十分
ある場合には空気熱源式低温ヒートポンプ５０を運転せ
ず、廃熱源式高温ヒートポンプ４０のみを運転すること
によって、成績係数が高い効率的な運転を行い、廃熱４
６の量が不足する場合には空気熱源式低温ヒートポンプ
５０と廃熱源式高温ヒートポンプ４０の双方を運転する
ことによって廃熱４６の発生時間や量が不安定であって
も負荷４７に安定して熱を供給し負荷を十分に加熱でき
る。In this heat pump device, when there is a sufficient amount of waste heat 46, the air heat source type low temperature heat pump 50 is not operated, and only the waste heat source type high temperature heat pump 40 is operated, thereby achieving efficient operation with a high coefficient of performance. waste heat 4
6 is insufficient, by operating both the air heat source type low temperature heat pump 50 and the waste heat source type high temperature heat pump 40, it is possible to stabilize the load 47 even if the generation time or amount of waste heat 46 is unstable. It can supply heat and sufficiently heat the load.
しかしながら、廃熱源式高温ヒートポンプ４０の加熱能
力は第５図に示すように、蒸発温度の変化によって大き
く増減し、例えば、凝縮温度が１２０℃で一定の場合蒸
発温度が７０℃から６０°Ｃに１０′″ｄｅｇ低下する
と、加熱能力が１２．８００Ｋｃａｌ／ｈから９８００
Ｋｃａｌ／ｈへ２３％も低下する。そこで、廃熱４６の
量が十分であってもその温度が変化する場合には空気熱
源式低温ヒートポンプ５０の運転・停止を繰り返さなけ
ればならず、そして、この運転・停止の繰り返しはエネ
ルギロスが大きく、また、空気の温度は廃熱４６の温度
より大巾に低いので空気熱源式低温ヒートポンプ５０の
エネルギ効率が悪いため、ヒートポンプ装置全体の効率
が低下してしまうという問題があった。However, as shown in FIG. 5, the heating capacity of the waste heat source type high-temperature heat pump 40 varies greatly depending on changes in the evaporation temperature. For example, when the condensation temperature is constant at 120°C, the evaporation temperature changes from 70°C to 60°C. When the heating capacity decreases by 10'''deg, the heating capacity decreases from 12.800Kcal/h to 9800Kcal/h.
Kcal/h decreases by 23%. Therefore, even if the amount of waste heat 46 is sufficient, if the temperature changes, the air heat source type low temperature heat pump 50 must be repeatedly operated and stopped, and this repeated operation and stop causes energy loss. Moreover, since the temperature of the air is much lower than the temperature of the waste heat 46, the energy efficiency of the air heat source type low temperature heat pump 50 is poor, resulting in a problem that the efficiency of the entire heat pump device is reduced.
（問題点を解決するための手段）
本発明は上記問題点に対処するために提案されたもので
あって、その要旨とするところは、高沸点冷媒を用いた
廃熱源式高温ヒートポンプにおける圧縮機をインバータ
駆動圧縮機となし、同ヒートポンプの廃熱を熱源とする
蒸発器と直列に補助蒸発器を設けるとともにこの補助蒸
発器の熱源となる低沸点冷媒を用いた空気熱源式低温ヒ
ートポンプを設け、廃熱量の変動に対してインバータ制
御で運転し、その制御範囲を越えると空気熱源式低温ヒ
ートポンプを運転するようにしたことを特徴とするヒー
トポンプ装置にある。(Means for Solving the Problems) The present invention has been proposed to address the above problems, and its gist is to is an inverter-driven compressor, an auxiliary evaporator is installed in series with the evaporator that uses the waste heat of the heat pump as a heat source, and an air-source low-temperature heat pump that uses a low boiling point refrigerant is installed as the heat source for the auxiliary evaporator. The heat pump device operates under inverter control in response to fluctuations in the amount of waste heat, and operates an air heat source type low-temperature heat pump when the amount of waste heat exceeds the control range.
（作用）
本発明においては上記構成を具えているため、廃熱源の
量又は温度の変動がインバータ制御範囲内にあるときは
空気ｐＢ式低温ヒートポンプの運転を行うことなく廃熱
源式高温ヒートポンプの圧縮機をインバータ制御するこ
とによってその加熱能力を確保する。廃熱源の量又は温
度がインバータの制御範囲を越えて低下した場合には空
気熱源式低温ヒートポンプを運転することによりヒート
ポンプ装置の加熱能力を確保する。(Function) Since the present invention has the above configuration, when the amount or temperature of the waste heat source is within the inverter control range, the air pB type low temperature heat pump is not operated and the waste heat source type high temperature heat pump is compressed. The heating capacity is ensured by controlling the machine with an inverter. When the amount or temperature of the waste heat source drops beyond the control range of the inverter, the heating capacity of the heat pump device is ensured by operating the air source type low temperature heat pump.
（実施例） 本発明の１実施例が第１図に示されている。(Example) One embodiment of the invention is shown in FIG.
第１図において、４０はＲ１１４等の高沸点冷媒を用い
た廃熱源式高温ヒートポンプで、電ａ４８からインバー
タ制御回路４９を介して駆動される圧縮機４１、凝縮器
４２、絞り装置４３、廃熱４６を熱源とする蒸発器４４
、この蒸発器４４と直列に設けられた補助蒸発２１Ｓ４
５からなる。５０はＲ１２、Ｒ２２等の低沸点冷媒を用
いた空気熱源式低温ヒートポンプで、圧縮ａ５１、補助
蒸発器４５を兼ねる凝縮器５２、絞り装置５３、空気を
熱源とする蒸発器５４、凝縮器５２の前後に配置された
開閉弁５５．５６からなる。In FIG. 1, 40 is a waste heat source type high temperature heat pump that uses a high boiling point refrigerant such as R114, and is driven by a compressor 41, a condenser 42, a throttle device 43, and a waste heat Evaporator 44 using 46 as a heat source
, an auxiliary evaporator 21S4 provided in series with this evaporator 44
Consists of 5. Reference numeral 50 is an air source type low temperature heat pump using a low boiling point refrigerant such as R12 or R22. It consists of on-off valves 55 and 56 arranged at the front and rear.
廃熱の量及び温度が十分でその変動中が小さいときは、
開閉弁５５．５６を閉とし圧縮機５１を停止することに
よって空気熱源式低温ヒートポンプ５０の運転を止め、
圧縮機４１を駆動することによって廃熱源式高温ヒート
ポンプ４０を運転する。When the amount and temperature of waste heat are sufficient and their fluctuations are small,
By closing the on-off valves 55 and 56 and stopping the compressor 51, the operation of the air heat source type low temperature heat pump 50 is stopped,
By driving the compressor 41, the waste heat source type high temperature heat pump 40 is operated.
すると、圧縮機４１から吐出された高沸点冷媒ガスは凝
縮器４２で負荷４７に熱を放出することによって凝縮し
た後、絞り装置４３で断熱膨張し、補助茶発器４５をこ
こで吸熱することなく流過して蒸発器４４に入り、ここ
で廃熱４６から吸熱することにより蒸発気化して圧縮６
４１に戻る。Then, the high boiling point refrigerant gas discharged from the compressor 41 is condensed in the condenser 42 by releasing heat to the load 47, and then adiabatically expanded in the expansion device 43, where the auxiliary tea generator 45 absorbs heat. It flows through the evaporator 44, where it absorbs heat from the waste heat 46, evaporates it, and compresses it.
Return to 41.
廃熱４６の量又は温度が低下することによって、負荷４
７への加熱能力が不足する場合にはインバータ制御回路
４９で駆動周波数を増大させることによって圧縮機４１
の能力を増大させて負荷４７への加熱能力を確保する。By reducing the amount or temperature of waste heat 46, load 4
If the heating capacity for the compressor 41 is insufficient, the inverter control circuit 49 increases the driving frequency.
The heating capacity for the load 47 is ensured by increasing the capacity of the load 47.
廃熱４６の量及び温度がインバータ制御回路４９の制御
範囲を越えて低下した場合には、開閉弁５５．５６を開
とし圧縮機５１を駆動して空気熱源式低温ヒートポンプ
５０を運転すると同時に圧縮機４１を駆動して廃熱源式
高温ヒートポンプ４０を運転する。When the amount and temperature of the waste heat 46 decreases beyond the control range of the inverter control circuit 49, the on-off valves 55 and 56 are opened and the compressor 51 is driven to operate the air source type low-temperature heat pump 50 and simultaneously start compression. The waste heat source type high-temperature heat pump 40 is operated by driving the heat pump 41.
すると、高沸点冷媒は上記と同様圧縮機４１、凝縮器４
２、絞り装置４３を経て補助蒸発器４５に入り、ここで
低沸点冷媒と熱交換して低沸点冷媒から熱を奪った後蒸
発器４４に入り、ここで廃熱４６から吸熱することによ
って蒸発気化して、圧縮機４１に戻る。一方、低沸点冷
媒は圧縮機５１から開閉弁５５を経て補助蒸発器４５を
兼ねる凝縮器５２に入り、ここで高沸点冷媒と熱交換し
て凝縮した後開閉弁５６を経て絞り装置５３で断熱膨張
し、次いで、庫発器５４で空気から吸熱することにより
蒸発気化した後、圧縮機４１に戻る。Then, the high boiling point refrigerant is transferred to the compressor 41 and the condenser 4 as described above.
2. It enters the auxiliary evaporator 45 through the throttling device 43, where it exchanges heat with the low boiling point refrigerant to remove heat from the low boiling point refrigerant, and then enters the evaporator 44, where it absorbs heat from the waste heat 46 and evaporates. It is vaporized and returned to the compressor 41. On the other hand, the low boiling point refrigerant passes through the on-off valve 55 from the compressor 51 and enters the condenser 52 which also serves as the auxiliary evaporator 45, where it exchanges heat with the high boiling point refrigerant and condenses. It expands, then evaporates by absorbing heat from the air in the storage generator 54, and then returns to the compressor 41.
（発明の効果）
本発明においては、廃熱の量又は温度の変動中が小さい
ときは空気熱源式低温ヒートポンプを運転せずに廃熱源
式高温ヒートポンプを運転し、その圧縮機をインバータ
制御することによって成績係数が高い効率的な運転を行
って所期の加熱能力を得ることができる。そして、廃熱
の量又は温度の変動中がインバータ制御範囲を越えると
空気熱源式低温ヒートポンプと廃熱源式高温ヒートポン
プを同時に運転することによって所期の加熱能力を得る
ことができる。この結果、廃熱の量又は温度が変動する
場合であってもその変動中が小さいときは空気熱源式低
温ヒートポンプの運転・停止を繰り返すことなく廃熱源
式高温ヒートポンプの圧縮機をインバータ制御すること
によって所期の加熱能力を得ることができるので、空気
熱源式低温ヒートポンプの運転・停止の頻度が少なくな
り、この運転・停止の繰り返しに伴うエネルギロスを少
なくでき、ヒートポンプ装置全体の効率を向上できる。(Effect of the invention) In the present invention, when the amount of waste heat or the fluctuation in temperature is small, the air heat source low temperature heat pump is not operated, but the waste heat source high temperature heat pump is operated, and its compressor is controlled by an inverter. This enables efficient operation with a high coefficient of performance to obtain the desired heating capacity. When the amount or temperature of waste heat fluctuates beyond the inverter control range, the desired heating capacity can be obtained by simultaneously operating the air heat source type low temperature heat pump and the waste heat source type high temperature heat pump. As a result, even if the amount or temperature of waste heat fluctuates, if the fluctuation is small, the compressor of the waste heat source high temperature heat pump can be controlled by the inverter without repeating the operation and stop of the air heat source low temperature heat pump. Because it is possible to obtain the desired heating capacity, the frequency of operation and stop of the air source type low-temperature heat pump can be reduced, the energy loss associated with repeated operation and stop can be reduced, and the efficiency of the entire heat pump device can be improved. .
第１図は本発明の１実施例を示す系統図、第２図ないし
第４図はそれぞれ従来のヒートポンプ装置の系統図、第
５図はヒートポンプの加熱能力と蒸発温度との関係を示
す線図である。
廃熱源式高温ヒートポンプ−４０、圧縮機−４１、イン
バータ制御回路−４８、芸発器−４４、廃熱−４６補助
蒸発器−４５、
凋−「−］
■−」
も ８幅穂只
三Fig. 1 is a system diagram showing one embodiment of the present invention, Figs. 2 to 4 are system diagrams of conventional heat pump devices, and Fig. 5 is a diagram showing the relationship between heat pump heating capacity and evaporation temperature. It is. Waste heat source high temperature heat pump-40, compressor-41, inverter control circuit-48, generator-44, waste heat-46 auxiliary evaporator-45,
Claims (1)
圧縮機をインバータ駆動圧縮機となし、同ヒートポンプ
の廃熱を熱源とする蒸発器と直列に補助蒸発器を設ける
とともにこの補助蒸発器の熱源となる低沸点冷媒を用い
た空気熱源式低温ヒートポンプを設け、廃熱量の変動に
対してインバータ制御で運転し、その制御範囲を越える
と空気熱源式低温ヒートポンプを運転するようにしたこ
とを特徴とするヒートポンプ装置。The compressor in a waste heat source high temperature heat pump using a high boiling point refrigerant is an inverter-driven compressor, and an auxiliary evaporator is installed in series with the evaporator, which uses the waste heat of the heat pump as a heat source, and serves as the heat source for this auxiliary evaporator. A heat pump characterized in that an air heat source low temperature heat pump using a low boiling point refrigerant is provided, the air heat source low temperature heat pump is operated under inverter control in response to fluctuations in the amount of waste heat, and when the control range is exceeded, the air heat source low temperature heat pump is operated. Device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10467986A JPH06100393B2 (en) | 1986-05-09 | 1986-05-09 | Heat pump device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10467986A JPH06100393B2 (en) | 1986-05-09 | 1986-05-09 | Heat pump device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62261865A true JPS62261865A (en) | 1987-11-14 |
| JPH06100393B2 JPH06100393B2 (en) | 1994-12-12 |
Family
ID=14387156
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10467986A Expired - Lifetime JPH06100393B2 (en) | 1986-05-09 | 1986-05-09 | Heat pump device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06100393B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004007224A1 (en) * | 2002-07-16 | 2004-01-22 | Toyota Jidosha Kabushiki Kaisha | Air-conditioning apparatus |
| WO2013035459A1 (en) * | 2011-09-08 | 2013-03-14 | 株式会社神戸製鋼所 | Heat pump |
-
1986
- 1986-05-09 JP JP10467986A patent/JPH06100393B2/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004007224A1 (en) * | 2002-07-16 | 2004-01-22 | Toyota Jidosha Kabushiki Kaisha | Air-conditioning apparatus |
| CN100408367C (en) * | 2002-07-16 | 2008-08-06 | 丰田自动车株式会社 | Air-conditioning apparatus |
| US7669647B2 (en) | 2002-07-16 | 2010-03-02 | Toyota Jidosha Kabushiki Kaisha | Air conditioning apparatus |
| WO2013035459A1 (en) * | 2011-09-08 | 2013-03-14 | 株式会社神戸製鋼所 | Heat pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06100393B2 (en) | 1994-12-12 |
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